Reaction type valve



Feb. 19, 1952 M, CASERTA 2,586,147

' REACTION TYPE VALVE Filed Aug. 7, 1947,

FTQ: 4f 44 fnl/Enfin* 3 vide a novel valve construction utilizing the reaction pressure exerted by overflow liquid to ald in maintaining substantially constant output pressure with varying input pressure of liquid.

Yet another object of my invention is the provision of readily adjustable means for exerting pressure on a standard poppet by-pass valve and upon an incremental effective area of adiaphragm associated with said valve.

Other and further important objects o'f this invention will be apparent from the disclosures in the specification and the accompanying drawings.

On the drawings:

Figure 1 is a vertical sectional view of my novel reaction-type valve construction showing the valve in closed position;

Figure 2 is an enlarged fragmentary sectional view of the upper portion of Figure 1, -with the valve in partially open position; and

Figure 3 is a horizontal sectional view of the valve structure taken substantially along the line III-III of Figure 1.

As shown on the drawings:

The reference numeral I indicates generally a fuel transfer mechanism, such as an aircraft fuel pump, with which is associated the relief valve assembly of my invention. Said pump comprises a pump casing II, and a valve housing cover I2 secured to said pump casing I I by means of bolts I3. The pump, as here diagrammatically illustrated, is of the rotary vane type and is generally designated by the reference numeral I4. The pump casing II is provided with an intake I5 and an outlet I6 for connecting the pump in a fuel line to an engine, or to any other point to which the fuel is to be delivered. Interiorly, the pump casing is divided by a transverse partition I1, on the intake side of which is formed a port I8 and on the outlet side of which is formed a port I9. In ow communication with ports I8 and I9 are upper circular passages and 2l, respectively, in the upper portion of the valve casing II. It will be understood, of course, that the port I9 is the inlet port of the relief valve and port I8 is the outlet port of the valve since flow of liquid through the valve is substantially opposite to that in the pump.

The upper portion of the pump casing II is formed with an axially concentric, cylindrical bore 22, which is in flow communication with the upper circular passage 20. The relief valve assembly comprises a cylindrical poppet-type valve member 23 mounted coaxially with respect to the cylindrical bore 22 for movement in said bore and in said passage 20 and having a diameter somewhat less than that of the bore 22. A second coaxial cylindrical bore 24 in the transverse partition I1 receives the snugly fitting cylindrical valve stem 25 for reciprocating sliding therein.

Referring now to Figure 2, the reference numeral 26 indicates generally a valve seat including a valve seat proper 26I adapted to cooperate with the -under surface of the valve member 23 to interrupt communication between the valve inlet port I9 and passage 2I, and the passage 20 and the valve outlet port I8. The valve seat 26 is formed as an annulus coaxially with respect to the valve member`23 and includes a portion of the upper surface of the transverse partition I1 and a portion of the bottom wall surface dening the upper circular passage 20. In the central portion of the valve seat is a circular ridge or bead 21, the function of which will be described in detail later in this specification. A complementary circular groove or channel 28 is formed in the seating surface of the valve member 23, the function of which will likewise be discussed below.

Radially inwardly and outwardly from the circular groove 28 of the valve member 23 are annular beveled surfaces 29 and 30. The beveled surface 29 slopes radially outwardly and axially upward toward the groove 28 tending to guide overflowing liquid from passage 2| into the groove 28. An annular space 3I is provided between the outer peripheral axially extending surface 32 of the valve member 23 and the inner axially extending bore defining surface 33 of the pump casing II and an outer annular recess 34 is formed in the top periphery of the valve member 23. It is to be understood that the stem 25 of the valve member 23 serves to maintain the valve member 23 in axial alignment for cooperation with the valve seat 26.

The cover I2, housing the pressure regulating mechanism of my invention, will now be described. A circular diaphragm 35 is clamped about its periphery between the lower anged end 36 of the housing cover I2 and the upper wall 31 of the valve housing II. Diaphragm 35 may suitably be formed of a natural or synthetic rubber composition. The annular recess 34 in the valve member 23 is adapted to leave unsupported an annular portion 38 of the diaphragm. An annular portion 39 of the diaphragm 35 resting on the upper wall 31, but not clamped between the lower flanged end 36 of the cover I3 and an outer annular portion 31 of the upper wall 31 of the valve housing I I, is freely supported by an inner annular portion 40 of the upper wall 31. It is apparent, therefore, that this annular portion 39 of the diaphragm 35, which is supported solely by the inner annular portion 40 of the upper wall 31, is free to move upwardly away from the supporting portion 40. A central portion 4I of the diaphragm 35 overlies the top surface portion of the valve member 23.

The top wall of the cover I2 is provided with a centralopening 4'2. A relief pressure regulating mechanism is housed within said cover I2 and comprises a pressure adjusting stud 43 having an upper end 44 projecting out of the cover I2 through said opening 42 and having a lower portion 45 threaded into an adjusting plate 46. The adjusting plate 46 has a pair of radial slots 41, 41 which engage vertically extending inwardly porjecting ribs, 4'8, 48 on the upper portion of the vertical walls of the cover I2. The projecting'ribs 48 thus serve to guide the adjusting plate 46 during reciprocating motion while preventing rotational motion thereof. As the projecting portion 44 of the threaded adjusting member 43 is turned, for instance, by means of a screw driver inserted into the kerf 49 in its upper projecting end 44, the adjusting plate 46 is held against rotation with and is confined to axial movement along the threaded adjusting member 4'3.

The adjusting plate 46 has a pair of progressively larger diameter annular steps. A spring 50 bears at its upper end against theinner annular step 5I and at its lower end against a circular plate 52 resting on the central portion 4I of the diaphragm 35. The circular plate 52 has a concentric circular ridge 53 serving to position the lowermost coil of the spring 50 on the outer peripheral portion of the plate 52. The outer annular step 54 of the adjusting plate 46 confines the upper end of a relatively heavy coil assent? spring 65 that lies-outside-ofspring 50 andrextends diwvnwardlyI coa-xiallywith thepressure adjustment member 43 to bear `against an annular plate 56 resting on the portion 39 of the upper wall-31 of the pump casing II. Theannular plate 56 has inner and outer peripheral beads 5-1 and 58, respectively, for positioning the spring l55 therebetween.

It will thus be apparentthattheamounts of compression of the springs 50 and 55- are simultaneously adjustable by-'means of thefadjusting plate 46 and the pressure adjustmentlmember 43. However, this is not necessary and it willbereadily apparentV to one skilled in the art that springs 50 andA 55' may lue-provided Withmeans for indi vi'dual' adjustment thereof.

Myl pressure regulating mechanism 4may be adapted to receive superchargerpressure by connecting theinterior of ther cover I2 tothe superchargcr (not shown), for instance, as byA means of -a' port `59 in boss 60` (Figure 3) formed on the cover I2. The effect of introducing supercharger pressure into the cover I2 will be readily apparent to those skilled in the art and need not be mentioned herein except to say that the super-v charger pressure will be useful in increasing the Outlet pressure in proportion thereto.

By reason of the above construction of the pressure regulating mechanism, the pressure adjustment member 43 can be so adjusted as to give the desired amount of pressure upon the valve member 23 so that. the relief valve will remain closed until that amount of pressure is exceeded. In normal operation, the pump takes fluid in through the intake I5 and'discharges it through the outlet I6. The amount of compression impressed upon the spring 59 by the adjustment of the pressure adjusting member 43 determines the pressure at the outlet side of the pump I4. When that pressure is exceeded, uid at the outlet side of said pump passes from the chamber I9 upwardly into the passage 2I against the underside 6| and the annular beveled surface39of the valve member 23, therebyl causing said Valve member to. be lifted from its' seat 26. Upward movement of the valve memberv 23 causes an upward movement of the central diaphragm portion, 4I against the. compressing force of the spring 59. The unseating of the valve member 23 provides a flowl passage for fluid from lthe delivery side of the pump into the upper circular passage 29 through the port I8, Vand then to the intake side of the pump. The pressure` on the outlet side of the pump I4 is thus relieved until a pressure below that forv whichv the regulating mechanism is set isagain reached, whereupon the valve ymember 23 is. caused to seatagainz under the action of the spring 59, as exerted through the central diaphragm portion 4 I.

In commonly known valve structures, includ.- ing, for instance, av valve with a 45 seat, as` the flow through the outlet side is less than the displacement. of the pump, the excess fluid. flows through the valve inlet port I9 .andl lifts-,valve member- 23 as much as is necessary to permit the overflow off excess fluid to the valve outlet port I8.. As the flow through passage I6 is increased the excessr fluid which must overflow through port, I9 is less, and correspondingly, the lift of valve member 23 is also less,4 as is the tension of spring 59. Therefore, the pressure of the fluid is, also correspondingly less. The, reverse occurs when the flow of the outlet side is decreased; It can generally be stated therefore that, in the known valve structures, ifA the `flowis increased 6| the` pressure decreases, while if the lflow-is de creased the pressure increases.

If, as issometimes desirable, `the same -pres su-re as that at which the pumpis normallyv supposed to deliver fuel at-the-outlet side is-applied at the-pump inlet, for instance, as attake-oif of an airplane as a precautionary measure, it isclear that there wouldbe no ow of fuel from-'the valve inlet port I9 to the valve outlet port I Il until la pressure differential Yis again established between the two ports. The excess of fluid pumped toward theI outlet willincrease thepressure in port I9 opening the valve and increasing the compression of spring 59', until the pressure differential between port I9 and port I8 sulficient to permit overflow from port I9 to port I8 of 'all the excessv fluid through the increased` opening between the valve member 23 and the valve seat 26.

In commonly known valve structures, Vthe greater the rate of spring (load necessaryto deflect the spring one inch), the greater will be' the increase in outlet pressure at the port `5, above the original setting, when the inl'et pressure is also raised to equal the original setting.

By increasing the size of the valve member with reference to the size and displacement of the pump so that a, slight movement of the valve member will produce large variations in the valve opening, and by decreasing the rate of the spring acting on the valve member so that movement of the valve member will produce very small variations in spring load, it has heretofore been normally possible to keep the variations in pressure at the outlet side within a very narrow range. In certain applications, however, and particularly in aircraft; space and weight are at a premium, and unfortunately increases in the size of the valve and in the weight of the spring mean increase in the size and weight of the whole system.

Furthermore, a large valve does not always seat properly and is more easily distorted. Also.` a high spring rate may mean a greater tendency of the valve to stick for mechanical reasons, thereby defeating its purpose.

I have discovered that if the valve is provided with the groove 28, and preferably if the valve seat is provided with a corresponding ridge 21 so that fluid is subjected to a change of direction. parallel to the axial movement of the valve as the fluid overflows from port I9 to. port I 8, the outlet pressure will. vary much'less when the flow is varied. As a matter of fact it is then possibleA` to hold the outlet pressure practically constant if the flow is variedfrom almost the maximum pump displacement to zero. This is explained as follows:

In standard poppetvalves it is only the static pressure of the fluid which by acting on lthe effective area of the valve member balances the spring tension. In my new valve, however; which for simplicity I call a reaction-type valve, bee

. cause of the reversal of directionof the uid flow,

an upward pressure is exerted in addition to the static pressure of the fluid on the effective valve area. The greater the mass of uid which impinges against the groove 28,` the greater the pressure so exerted on the valve member 23 tending to move valve member 23 upwardly against the spring compression. Equilibrium is reached when the spring compression equals the static pressure plusv the dynamic pressure exerted on thevalve member by-the fluid.

When, however, the flowJ decreases, the dytiamic pressure exerted by the fluid also decreases while the static pressure is affected very little bythe now. --As compared with standard poppet valves we then have a more rapid decrease of the total fluid pressure against the valve, and therefore the reaction type valve will close more than the standard valve would. This, on the other hand, means a greater restriction in the passage between port I9 and port I8 and therefore an increase in the pressure inport I9 as compared to the vpressure that would prevail with a standard valve. In other words, the outlet pressure will drop less and the valve member 23 will move more, much in the same manner as if the spring U had a lower rate.

. Conversely, if the now through the outlet side isrestricted so that the overflow from port I9 to'port I8 must increase, owing to the increased mass of the overflowing fluid. the dynamic load on the valve will increase rapidly and the valve member 23 will move more than a poppet valve of standard design would move for a given pressure'variation. This also means that the outlet pressure will not increase as much as it would with a standard poppet valve.

The operation of the reaction-type valve when the inlet pressure is being increased up'to the original setting of the outlet pressure, while the outlet iiow remains constant and the overflow also remains constant is analyzed as follows. The increased opening of the valve to discharge the overflow from port I9 to port I8 under increasingly lower pressure differential must be due only to increase in static pressure. Furthermore, as the velocity of the fluid through the valve at low pressure differential will be low, the reaction will in fact be less than under conditions of original setting when the pressure differential was higher and the velocity was higher. ATherefore the dynamic feature of the reaction valve so far described would not by itself improve the performance under this analysis.

y To correct this situation, I introduce additional improvements to the ordinary diaphragmbalanced poppet valve.

= According to standard practice it is usually desirable to make the effective diameter of the balancing diaphragm substantially equal to the effective diameter of the valve. In Figure 2, in order for the diaphragm 35 to have an effective diameter substantially equal to the effective diameter of the Valve member 23, the diaphragm must be'clamped over the ent-ire top area of the upper wall 3'I of the pump housing Il. On the other hand, in orderV to have an effective diameter larger than that of the valve member 23, while supporting the diaphragm 35 by the entire wall portion 31, I securely clamp it all around only at an outer portion 3l by the bottom flange wall 35of the cover l2. The annular portion 39 of the diaphragm supported by the wall portion 4U is pressed downwardly by spring 55 under the action of the adjusting plate 46, which is in the present embodiment the same adjusting plate as for the spring 50. y

It will be seen that my diaphragm 35 will usually give the same performance as the diaphragm clamped over the entire wall portion 3i', if the pressure on the inlet side is reduced below the original setting pressure or if supercharger pressure is applied to the top of the diaphragm. If, howeven'the inlet pressure is increased, spring 55 is so proportioned that, as the inlet pressure nears the outlet pressure, ring 5S begins to move upwardly, and as a consequence the effective diameter ofthe diaphragm 35 increases, thereby allowing easier opening of the valve and perJ mitting the overflow of fluid from outlet to inlet'l without excessive increase in outlet presusre.

The rate of the spring 55 is preferably so proportioned with reference to the rate of spring 50 and in relation to the pressure exerted by the fluid on the portion of the diaphragm 39 supported by wall portion 40 that approximately the same action will occur Whatever the original pressure setting. l

It could, of course, be so proportioned as to have different actions for different settings and, in fact, a separate adjustment could be provided for spring 55 independently from plate 46.

Returning now to the reaction-type valve, I can say that while, according to my tests, the combination shown seems to give best results, I have noticed that it is not necessary to give both the valve and the valve seat the very definite' shape shown in the drawings and that some reac'-' tion performance can be obtained, for instance, by leaving the valve with a 45 conical seat and' modifying the seat alone; or conversely, byleaving the valve seat flat and providing only the valve with a groove.

The best combination for each application is best determined by experimentation. I may add that the configuration of the valve member 23, shown in the drawings, seems also to improve the freedom of movement of the valve member and reduce any tendency to sticlz,` thus further effectively improving actual valve performance. This may be due to a floating action of the reversing stream, which tends to keep the valve centrally floated within the seat opening. l

It will, of course, be understood that variousl details of construction may be varied through a wide range without departing from the prin- 'said cylindrical relief port to open and close said port, a circular balancing diaphragm exposed to liquid pressure in the outlet passage attached to said valve member and supported on one face so as to have substantially an eifective diameter equal to the effective diameter of the cylindrical valve member a clamping ring engaging extreme outer portion of said diaphragm leaving an unclamped intermediate portion, and resilient means acting to maintain the effective diameter substantially equal to that of the valve member, whereby upon substantial increase in liquid pressure in said outlet said resilient means will yield so that the unclamped intermediate portion of the diaphragm is presented to the overflow liquid.

2. A diaphragm-balanced relief valve comprising al housing defining an inlet and an outlet passage and a cylindrical port in communication with said inlet and outlet passages, a valve member adapted for movement in a relief port having a surface adapted to cooperate with a valve seat', said valve seat having a ridge thereon, and said surface of said valve member having a groove `complementary to said ridge for utilizingthe dy- I lamic reaction` of overflowing liquid againstrs'aid complementary groove to exert a dynamic valveopening pressure on said valve member, a balancing diaphragm attached to the top of said valve member, housing means clamping the extreme. outer portion of the diaphragm and supporting an intermediate diaphragm portion, and resilient means acting on said intermediate diaphragm portion.

3. A relief valve for a cylindrical relief port E a circular coaxial groove complementary to said circular ridge, a diaphragm having a central circular portion secured to the circular top surface of said valve member, housing means clamping the extreme outer portion of said diaphragm and supporting an intermediate annular diaphragm portion, a first relatively light compression spring acting on the central portion of said diaphragm and through the diaphragm on the valve member, a second compression spring surrounding said first spring and acting on the intermediate supported annular portion of said diaphragm, means for adjusting the compression of said rst spring for controlling the inlet pressure ofsaid valve, and means for adjusting the compression of said second spring.

4. A relief valve comprising an open-topped housing dening an inlet and an outlet passage and having a cylindrical port therein, a poppettype valve having a groove in a flow exposed surface thereof, and annular surface exposed to fluid in said inlet passage and a cylindrical stem,

a cylindrical bore coaxial of said port slidably receiving said stem for centering of said valve, a diaphragm extending across the top of said housing and having a central portion secured to said valve and an outer portion supported by said housing, a hollow cover clamping an outer part of said outer portion of said diaphragm leaving the inner part of the outer portion freely supported by said housing, and "a selectively adjustable compression spring acting on the inner part of the outer portion of said diaphragm.

5. The relief valve of claim 4 wherein the cover has a passage for receiving a supercharger connection. Y

6. A relief valve comprising a housing having a cylindrical opening in the top thereof, a'coaxial i cylindrical valve port therein inlet and outlet passages connecting with said valve port and a coaxial cylindrical bore below said port, a poppet-type valve reciprocating freely in said cylindrical opening and having a stem snugly fitting into said bore for alignment of said valve, a valve seat including a coaxial circular triangular cross-sectional ridge surrounding saidvalve port, said valve having a complementary V- shaped groove, a. diaphragm extending across the top of said housing exposed to said outlet passage and having a central portion engaging the top of the valve and an outer portion supported by said housing, a cover clamping an outer part of said outer portion of vsaid diaphragm against the top of said housing, an lnner part of said outer portion of said diaphragm resting on the top of said housing, a flrstspring in said cover acting on said central "portion of said diaphragm, and a second spring in said cover urging said inner part of said outer portion of said diaphragm against said top.

7. A relief valve assembly comprising a housing providing an inlet and an outlet passage and a cylindrical port therebetween in communication threwith and provided with an annular seat, a valve for said seat, a diaphragm clamped at its periphery to said housing and at its central portion to said valve, there being an intermediate annular diaphragm portion supported by said housing but exposed to pressure in the inlet passage when said valve is closed, first resilient means biasing said valve toward closed position and second resilient means biasing said intermediate diaphragm portion into housingsupported relationship, whereby when inlet pressure overbalances the biasing effect of said second resilient means the intermediate annular diaphragm portion is forced out of supporting contact with said housing to increase the effective diameter of said diaphragm and thereby aid in the opening of said valve when the outlet pressure overbalances the biasing force of said first resilient means.

8. A relief valve assembly comprising a housing providing an inlet and outlet passage and a port therebetween in communication therewith and provided with an annular seating ridge, a valve member controlling said port and having an annularly grooved surface for seating against said seating ridge, a diaphragm peripherally clamped to said housing and centrally clamped to said valve member, there being an intermediate annular diaphragm portion supported by but not clamped to said housing and exposed to fluid in the inlet passage when said valve is closed, and rst and second springs biasing said valve toward closed position and biasing said intermediate annular diaphragm portion toward housing-supported position, respectively, the overbalancing of the second spring by fluid pressure in said inlet passage aiding the opening of said valve by increasing the effective diaphragm area subject to pressure of the fluid in said outlet passage and said grooved surface aiding in the unseating of said valve by pressure thereagainst of the fluid in said outlet passage.

9. A relief valve for relieving excessive pressure by fluid flow from a high to a low pressure chamber, a valve controlling ow between the high and the low pressure chambers, a first spring biasing said valve to closed position, a diaphragm attached to and movable with said valve and having an unattached portion subject to fluid pressure in said low pressure chamber when said valve is closed and a second spring resisting .movement of such unattached portion when subjected to such fluid pressure up to a predetermined value but thereafter yielding to subject a greater area of said diaphragm to such fluid pressure and thus assist in opening said valve.

MICHELE CASERTA.

REFERENCES CITED The following references are of record in the rile of this patent:

UNITED STATES PATENTS Number Name Date 291,013 Richardson Dec. 25, 1883 342,267 Richardson May 18, 1886 1,200,875 Roy Oct. 10, 1916 

